JP6269615B2 - Differential device for vehicle - Google Patents

Differential device for vehicle Download PDF

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Publication number
JP6269615B2
JP6269615B2 JP2015157740A JP2015157740A JP6269615B2 JP 6269615 B2 JP6269615 B2 JP 6269615B2 JP 2015157740 A JP2015157740 A JP 2015157740A JP 2015157740 A JP2015157740 A JP 2015157740A JP 6269615 B2 JP6269615 B2 JP 6269615B2
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ring gear
opening
rotation axis
inner peripheral
differential
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JP2017036780A (en
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孝 木天
孝 木天
典弘 溝口
典弘 溝口
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Toyota Motor Corp
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Toyota Motor Corp
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Priority to JP2015157740A priority Critical patent/JP6269615B2/en
Priority to US15/220,831 priority patent/US10012302B2/en
Priority to MYPI2016702756A priority patent/MY183853A/en
Priority to BR102016017652A priority patent/BR102016017652A2/en
Priority to KR1020160098398A priority patent/KR101846691B1/en
Priority to CN201610633149.2A priority patent/CN106438922B/en
Priority to EP16182671.4A priority patent/EP3128208B1/en
Priority to RU2016132132A priority patent/RU2638341C1/en
Publication of JP2017036780A publication Critical patent/JP2017036780A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/08—Profiling
    • F16H55/0886—Profiling with corrections along the width, e.g. flank width crowning for better load distribution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/037—Gearboxes for accommodating differential gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H2048/385—Constructional details of the ring or crown gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H2055/173—Crown gears, i.e. gears have axially arranged teeth

Description

本発明は、開口を有するディファレンシャルケース（以下、デフケースと略記）を備えた車両用ディファレンシャル装置に関し、とりわけ、デフケースから発生するギヤノイズを抑制する技術に関する。   The present invention relates to a differential apparatus for a vehicle including a differential case having an opening (hereinafter abbreviated as a differential case), and more particularly to a technique for suppressing gear noise generated from the differential case.

車両用ディファレンシャル装置の一種に、一対のサイドギヤおよびそれと噛み合うピニオンギヤを収容する周壁と前記リングギヤを固定するために前記周壁から外周側へ突設された環状のリングギヤ取付部と前記周壁の一部に内外を貫通して形成された開口とを有し、一回転軸線まわりに回転させられるデフケースと、前記周壁の外側に装着され、前記回転軸線を中心とする円環状のリングギヤ、とを有するものが知られている。たとえば、特許文献１の車両用ディファレンシャル装置がそれである。特許文献１の車両用ディファレンシャル装置では、円環状の前記リングギヤ取付部の取付面に固定された円環状のリングギヤに入力された動力が、前記一対のサイドギヤの回転差を許容しつつそれら一対のサイドギヤにそれぞれ連結された左右一対の駆動輪へ伝達される。   A kind of differential device for a vehicle includes a peripheral wall that houses a pair of side gears and a pinion gear meshing with the side gear, an annular ring gear mounting portion that protrudes from the peripheral wall to the outer peripheral side to fix the ring gear, and a part of the peripheral wall. And a differential case that is rotated around one rotation axis, and an annular ring gear that is mounted outside the peripheral wall and that is centered on the rotation axis. It has been. For example, the differential apparatus for vehicles of patent document 1 is it. In the differential apparatus for a vehicle disclosed in Patent Document 1, power input to an annular ring gear fixed to an attachment surface of the annular ring gear attachment portion allows the pair of side gears while allowing a rotational difference between the pair of side gears. Are transmitted to a pair of left and right drive wheels connected to each other.

特開２０１１−１０６５０４号公報JP 2011-106504 A

ところで、特許文献１のような車両用ディファレンシャル装置では、デフケースの周壁の一部が開口しており、前記周壁のうち前記開口周辺は応力が掛かりやすく、前記リングギヤのうち前記開口周辺に取り付けられる前記リングギヤの歯面にも応力が掛かりやすい。そのため、リングギヤに高トルクが入力されると、デフケースとリングギヤとの組立体において前記リングギヤのうち前記開口周辺に取り付けられる前記リングギヤの歯面は、リングギヤの他の部位よりも変形し易く、リングギヤとリングギヤにトルクを入力させるドライブギヤとの間で局部的に噛合面積が変化するおそれがあり、このような噛合面積の変化によって、ギヤノイズが増大する可能性がある。   By the way, in the differential apparatus for vehicles like patent document 1, a part of peripheral wall of a differential case is opening, The opening periphery of the said peripheral wall is easy to apply stress, The said ring gear is attached to the said periphery of said opening. Stress is easily applied to the tooth surface of the ring gear. Therefore, when a high torque is input to the ring gear, the tooth surface of the ring gear attached to the periphery of the opening of the ring gear in the assembly of the differential case and the ring gear is more easily deformed than other parts of the ring gear, There is a possibility that the meshing area locally changes with the drive gear that inputs torque to the ring gear, and such a change in the meshing area may increase gear noise.

本発明は、以上の事情を背景として為されたものであり、その目的とするところは、リングギヤのドライブギヤとの噛合い面積が変化することにより発生するギヤノイズを抑制する車両用ディファレンシャル装置を提供することにある。   The present invention has been made in the background of the above circumstances, and an object of the present invention is to provide a vehicle differential device that suppresses gear noise generated when the meshing area of the ring gear with the drive gear changes. There is to do.

上記目的を達成するための本発明の要旨とするところは、一対のサイドギヤおよび該サイドギヤと噛合うピニオンギヤを収容する周壁と該周壁の一部に内外を貫通して形成された開口とを有し、一回転軸線まわりに回転させられるデフケースと、前記周壁の外側に装着され、前記回転軸線を中心とする円環状のリングギヤとを、備えた車両用ディファレンシャル装置において、前記リングギヤの内周縁部のうち、前記開口が貫通する方向から見たときに前記開口の一部を覆うように構成され、前記開口の一部を覆わない内周縁部に比べて前記開口側に突出した突出部を有することにある。   In order to achieve the above object, the gist of the present invention includes a pair of side gears and a peripheral wall that accommodates a pinion gear that meshes with the side gear, and an opening formed through a part of the peripheral wall from inside and outside. In the differential device for a vehicle, comprising: a differential case that is rotated around one rotation axis; and an annular ring gear that is mounted outside the peripheral wall and that is centered on the rotation axis. The projection is configured to cover a part of the opening when viewed from the direction through which the opening penetrates, and has a protruding portion that protrudes toward the opening compared to an inner peripheral edge that does not cover a part of the opening. is there.

このように構成された本発明の車両用ディファレンシャル装置によれば、前記リングギヤの内周縁部のうち、前記開口が貫通する方向から見たときに前記開口の一部を覆うように構成され、前記開口の一部を覆わない内周縁部に比べて前記開口側に突出した突出部を有する。そのような突出部を有するリングギヤとデフケースとの組立体において、リングギヤのうち前記開口の前記回転軸線まわりの角度範囲内の径方向の幅寸法を増やすことにより剛性が高くされることから、リングギヤのドライブギヤとの噛合面積が変化することによるギヤノイズが抑制される。また、リングギヤの突出部は、デフケースの開口側へ突出したものであるため、デフケースおよびリングギヤの組立体が大きくなることはない。このため、リングギヤとデフケースとの組立体の剛性が高くされるとともにディファレンシャル装置全体の小型化が達成される。   According to the vehicle differential device of the present invention configured as described above, the inner periphery of the ring gear is configured to cover a part of the opening when viewed from the direction in which the opening penetrates, Compared to the inner peripheral edge that does not cover a part of the opening, it has a protruding portion protruding toward the opening. In the ring gear and differential case assembly having such a protrusion, the rigidity of the ring gear is increased by increasing the radial width within the angular range around the rotation axis of the opening. Gear noise due to a change in the meshing area with the gear is suppressed. Moreover, since the protrusion part of a ring gear protrudes to the opening side of a differential case, the assembly of a differential case and a ring gear does not become large. For this reason, the rigidity of the assembly of the ring gear and the differential case is increased, and the entire differential device is reduced in size.

ここで、好適には、前記リングギヤの歯幅は、前記突出部では、それ以外の部分よりも拡大される。この場合には、リングギヤとドライブピニオンとの噛合位置がリングギヤにおける前記突出部の側へずれた場合でも、前記ドライブピニオンは前記リングギヤの前記突出部の歯幅の拡大された噛合歯と噛合うことより、リングギヤとドライブピニオンとの噛合面積の低下が抑制されて、ギヤノイズの発生が低減される。また、ドライブピニオンとの噛合面積の低下によるリングギヤの噛合歯への単位面積当りの入力が大きくなることが抑制されることから、リングギヤの耐久性を向上することができる。   Here, it is preferable that the tooth width of the ring gear is larger in the protruding portion than in other portions. In this case, even when the meshing position of the ring gear and the drive pinion is shifted to the projecting portion side of the ring gear, the drive pinion is meshed with the meshing tooth whose tooth width of the projecting portion of the ring gear is increased. As a result, the reduction of the meshing area between the ring gear and the drive pinion is suppressed, and the generation of gear noise is reduced. Further, since the input per unit area to the meshing teeth of the ring gear due to the decrease in the meshing area with the drive pinion is suppressed, the durability of the ring gear can be improved.

本発明の一実施例の車両用ディファレンシャル装置の回転軸線Ｃ１を含む断面を示す斜視図である。It is a perspective view which shows the cross section containing the rotating shaft line C1 of the differential apparatus for vehicles of one Example of this invention. 図１の車両用ディファレンシャル装置の回転軸線Ｃ１を含み、ピニオンピンの中心線と垂直な断面の一部を示す斜視図である。It is a perspective view which shows a part of cross section perpendicular | vertical to the centerline of a pinion pin including the rotation axis C1 of the differential apparatus for vehicles of FIG. 図１の車両用ディファレンシャル装置の回転軸線Ｃ１方向に視た正面図である。FIG. 2 is a front view of the vehicle differential apparatus of FIG. 1 viewed in the direction of a rotation axis C1. 図１の車両用ディファレンシャル装置の斜視図である。It is a perspective view of the differential apparatus for vehicles of FIG. 図１のリングギヤを回転軸線Ｃ１方向に視た正面図である。It is the front view which looked at the ring gear of Drawing 1 in the direction of rotation axis C1. 図５のリングギヤのＶＩ−ＶＩ視断面図である。FIG. 6 is a cross-sectional view of the ring gear of FIG. 図５のリングギヤのＶＩＩ−ＶＩＩ視断面図である。FIG. 7 is a cross-sectional view of the ring gear of FIG. 5 taken along the line VII-VII. 図５のリングギヤを回転軸線Ｃ１方向に垂直な平面に射影した際の射影を示す図である。It is a figure which shows the projection at the time of projecting the ring gear of FIG. 5 on the plane perpendicular | vertical to the rotation axis C1 direction. 本発明の他の実施例の車両用ディファレンシャル装置のリングギヤを回転軸線Ｃ１方向に垂直な平面に射影した際の射影を示す図である。It is a figure which shows the projection at the time of projecting the ring gear of the differential apparatus for vehicles of the other Example of this invention on the plane perpendicular | vertical to the rotation axis C1 direction. 本発明の他の実施例の車両用ディファレンシャル装置のリングギヤを回転軸線Ｃ１方向に垂直な平面に射影した際の射影を示す図である。It is a figure which shows the projection at the time of projecting the ring gear of the differential apparatus for vehicles of the other Example of this invention on the plane perpendicular | vertical to the rotation axis C1 direction. 本発明の他の実施例の車両用ディファレンシャル装置のリングギヤを回転軸線Ｃ１方向に垂直な平面に射影した際の射影を示す図である。It is a figure which shows the projection at the time of projecting the ring gear of the differential apparatus for vehicles of the other Example of this invention on the plane perpendicular | vertical to the rotation axis C1 direction.

以下、本発明の車両用ディファレンシャル装置の一実施例について図面を参照して詳細に説明する。   Hereinafter, an embodiment of a differential device for a vehicle according to the present invention will be described in detail with reference to the drawings.

図１は、本発明の一実施例の車両用ディファレンシャル装置１０（以下、「ディファレンシャル装置１０」という。）のデフケース２６の回転軸線Ｃ１およびピニオンピン３０の中心線を通る断面を示す斜視図である。図２は、ディファレンシャル装置１０のデフケース２６の回転軸線Ｃ１を通り、ピニオンピン３０の中心線に垂直な断面の一部を示す斜視図である。図３は、ディファレンシャル装置１０の回転軸線Ｃ１方向に視た図であるとともに、リングギヤ２８と噛み合うドライブピニオン１３およびドライブピニオンシャフト１２の断面を併せて示す図である。図４は、ディファレンシャル装置１０の斜視図である。なお、リングギヤ２８に形成された噛合歯１６（図６および図７に示す。）はたとえばハイポイドギヤであるが図１から図４では省略されている。また、図１および図２では、サイドギヤ１８と動力伝達可能に連結される車軸は、図示されていない。ディファレンシャル装置１０は、回転軸線Ｃ１上において相対向する一対のサイドギヤ１８、および回転軸線Ｃ１を挟んで相対向し且つ上記一対のサイドギヤ１８にそれぞれ噛み合う一対のピニオンギヤ２０を、それぞれ回転可能に支持した状態で収容する円筒状の周壁２２と周壁２２の外周面から外周側へ回転軸線Ｃ１に直交する方向に一体に突設され、リングギヤ取付部として機能する円環状のフランジ部２４とを有し、一回転軸線Ｃ１まわりに回転させられるデフケース２６と、そのフランジ部２４の一面である円環状の取付面２７に固定された円環状のリングギヤ２８とを、備えている。すなわち、リングギヤ２８は、その中心がデフケース２６の回転軸線Ｃ１と同心に周壁２２の外側に装着されている。デフケース２６の内部において一対のピニオンギヤ２０を回転可能に支持するピニオンピン３０の両端部が、その長手方向がリングギヤ２８の回転軸線Ｃ１と直交するように周壁２２の回転軸線Ｃ１方向の中央に固定されている。また、デフケース２６は、周壁２２から回転軸線Ｃ１方向に互いに離隔する方向に突設された円筒状の一対のボス部３２を備えている。これらボス部３２に図示しない一対の車軸の一端部がそれぞれ挿入され、デフケース２６内で一対のピニオンギヤ２０を挟む一対のサイドギヤ１８のそれぞれとスプライン嵌合により動力伝達可能に連結されている。フランジ部２４は、デフケース２６の周壁２２の回転軸線Ｃ１方向におけるピニオンピン３０とボス部３２との間の外周面から外周側へ突設されており、リングギヤ２８は、フランジ部２４のピニオンピン３０側の環状の取付面２７に面接触した状態で周方向に等間隔に配置された複数本（たとえば１６本）のボルト３４によりフランジ部２４に固定されている。   FIG. 1 is a perspective view showing a cross section passing through a rotation axis C1 of a differential case 26 and a center line of a pinion pin 30 of a vehicle differential apparatus 10 (hereinafter referred to as “differential apparatus 10”) according to an embodiment of the present invention. . FIG. 2 is a perspective view showing a part of a cross section passing through the rotation axis C <b> 1 of the differential case 26 of the differential device 10 and perpendicular to the center line of the pinion pin 30. FIG. 3 is a view of the differential device 10 as viewed in the direction of the rotation axis C <b> 1, and also shows a cross section of the drive pinion 13 and the drive pinion shaft 12 that mesh with the ring gear 28. FIG. 4 is a perspective view of the differential device 10. The meshing teeth 16 (shown in FIGS. 6 and 7) formed on the ring gear 28 are hypoid gears, for example, but are omitted in FIGS. Further, in FIGS. 1 and 2, the axle connected to the side gear 18 so as to be able to transmit power is not shown. The differential device 10 rotatably supports a pair of side gears 18 opposed to each other on the rotation axis C1 and a pair of pinion gears 20 opposed to each other across the rotation axis C1 and meshed with the pair of side gears 18, respectively. A cylindrical peripheral wall 22 and an annular flange portion 24 projecting integrally from the outer peripheral surface of the peripheral wall 22 to the outer peripheral side in a direction perpendicular to the rotation axis C1 and functioning as a ring gear mounting portion. A differential case 26 rotated around the rotation axis C <b> 1 and an annular ring gear 28 fixed to an annular mounting surface 27 that is one surface of the flange portion 24 are provided. That is, the ring gear 28 is mounted on the outside of the peripheral wall 22 so that the center thereof is concentric with the rotation axis C <b> 1 of the differential case 26. Both ends of the pinion pin 30 that rotatably supports the pair of pinion gears 20 inside the differential case 26 are fixed to the center of the peripheral wall 22 in the direction of the rotation axis C1 so that the longitudinal direction thereof is orthogonal to the rotation axis C1 of the ring gear 28. ing. Further, the differential case 26 includes a pair of cylindrical boss portions 32 protruding from the peripheral wall 22 in the direction away from each other in the direction of the rotation axis C1. One end portion of a pair of axles (not shown) is inserted into the boss portions 32, and is connected to each of the pair of side gears 18 sandwiching the pair of pinion gears 20 in the differential case 26 by spline fitting. The flange portion 24 protrudes from the outer peripheral surface between the pinion pin 30 and the boss portion 32 in the direction of the rotation axis C1 of the peripheral wall 22 of the differential case 26 to the outer peripheral side, and the ring gear 28 is connected to the pinion pin 30 of the flange portion 24. It is fixed to the flange portion 24 by a plurality of (for example, 16) bolts 34 arranged at equal intervals in the circumferential direction in surface contact with the annular mounting surface 27 on the side.

図２から図４において示されるように、デフケース２６には、周壁２２の側面の一部にデフケース２６の内外を貫通して形成された一対の開口３６が形成されている。この一対の開口３６は、ピニオンピン３０を挟んで円筒状の周壁２２の側面を局所的に切り欠くように形成されている。   As shown in FIGS. 2 to 4, the differential case 26 is formed with a pair of openings 36 formed through a part of the side surface of the peripheral wall 22 so as to penetrate the inside and outside of the differential case 26. The pair of openings 36 are formed so as to locally cut out the side surface of the cylindrical peripheral wall 22 with the pinion pin 30 interposed therebetween.

図３において示されるように、ディファレンシャル装置１０は、例えば車両の駆動源からの動力を一対の駆動輪に伝達する動力伝達経路に設けられ、プロペラシャフトに連結されたドライブピニオンシャフト１２およびその一端に設けられたドライブピニオン１３を備えている。ドライブピニオンシャフト１２は、第１軸受１４および第２軸受１５を介して図示しないハウジングに回転軸線Ｃ２回りに回転可能に支持されている。ドライブピニオンシャフト１２の回転軸線Ｃ２は、リングギヤ２８の回転軸線Ｃ１と直角であるが交差しない立体交差の関係にあり、ドライブピニオン１３とそれに噛合うリングギヤ２８とは、ハイポイドギヤ対である。ディファレンシャル装置１０は、ドライブピニオン１３からリングギヤ２８に入力された動力を一対のサイドギヤ１８の回転差を許容しつつそれら一対のサイドギヤ１８にそれぞれ連結された左右一対の車軸に伝達する。   As shown in FIG. 3, the differential device 10 is provided in a power transmission path that transmits power from a driving source of a vehicle to a pair of driving wheels, for example, and is connected to a drive pinion shaft 12 connected to a propeller shaft and one end thereof. A drive pinion 13 is provided. The drive pinion shaft 12 is supported by a housing (not shown) via a first bearing 14 and a second bearing 15 so as to be rotatable around a rotation axis C2. The rotation axis C2 of the drive pinion shaft 12 is in a three-dimensional crossing relationship that is perpendicular to the rotation axis C1 of the ring gear 28 but does not intersect, and the drive pinion 13 and the ring gear 28 meshing with it are a hypoid gear pair. The differential device 10 transmits power input from the drive pinion 13 to the ring gear 28 to a pair of left and right axles connected to the pair of side gears 18 while allowing a rotational difference between the pair of side gears 18.

図５は、リングギヤ２８を回転軸線Ｃ１方向に視た図であり、図６は、図５のＶＩ−ＶＩ視断面図であり、図７は、図５のＶＩＩ−ＶＩＩ視断面図である。円環状のリングギヤ２８は、図７に示されるように、回転軸線Ｃ１方向から視たときに、フランジ部２４の取付面２７と当接する側とは反対側の内周縁部３８と外周縁部４０との間の円錐面上に歯幅ａの噛合歯１６を複数有し、その噛合歯１６がリングギヤ２８よりも小径であるドライブピニオン１３の噛合歯と噛合わされている。リングギヤ２８のフランジ部２４との当接面には、ボルト３４と螺合する雌ネジが形成された円柱状穴４２が周方向に複数形成されている。なお、図５において、リングギヤ２８の円錐面上に形成された噛合歯１６は省略されている。また、デフケース２６とリングギヤ２８は、ボルトではなく溶接されることで、組み付けられてもよい。   5 is a view of the ring gear 28 as viewed in the direction of the rotation axis C1, FIG. 6 is a sectional view taken along line VI-VI in FIG. 5, and FIG. 7 is a sectional view taken along line VII-VII in FIG. As shown in FIG. 7, the annular ring gear 28 has an inner peripheral edge portion 38 and an outer peripheral edge portion 40 on the opposite side to the side in contact with the mounting surface 27 of the flange portion 24 when viewed from the direction of the rotation axis C <b> 1. A plurality of meshing teeth 16 having a tooth width a are provided on the conical surface between the two and the meshing teeth 16 are meshed with the meshing teeth of the drive pinion 13 having a smaller diameter than the ring gear 28. On the contact surface of the ring gear 28 with the flange portion 24, a plurality of cylindrical holes 42 formed with female threads that are screwed into the bolts 34 are formed in the circumferential direction. In FIG. 5, the meshing teeth 16 formed on the conical surface of the ring gear 28 are omitted. The differential case 26 and the ring gear 28 may be assembled by welding instead of bolts.

ところで、デフケース２６は、周壁２２に一対の開口３６を有しているため、周壁２２のうち開口３６周辺は応力が掛かりやすく、リングギヤ２８のうち開口３６周辺の歯面にも応力が掛かりやすい。そのため、リングギヤ２８に高負荷が入力されると、フランジ部２４に固定されたリングギヤ２８のうちの開口３６の回転軸線Ｃ１まわりの角度範囲内の部分すなわち開口３６付近に形成された噛合歯１６において最も撓みが大きくなり、リングギヤ２８とドライブピニオン１３との噛合面積が局所的に変化する可能性があった。そのため、ディファレンシャル装置１０には、装置自体の小型化と、デフケース２６とリングギヤ２８との組立体においてリングギヤ２８のドライブピニオン１３との噛合面積が変化することにより発生するギヤノイズの抑制とを両立することが望まれていた。   By the way, since the differential case 26 has a pair of openings 36 in the peripheral wall 22, stress is easily applied to the periphery of the opening 36 in the peripheral wall 22, and stress is also easily applied to the tooth surface of the ring gear 28 around the opening 36. Therefore, when a high load is input to the ring gear 28, the portion of the ring gear 28 fixed to the flange 24 within the angular range around the rotation axis C <b> 1 of the ring 36, that is, the meshing teeth 16 formed in the vicinity of the opening 36. There is a possibility that the deflection becomes the largest and the meshing area between the ring gear 28 and the drive pinion 13 changes locally. Therefore, the differential device 10 is compatible with both miniaturization of the device itself and suppression of gear noise generated by changing the meshing area of the ring gear 28 with the drive pinion 13 in the assembly of the differential case 26 and the ring gear 28. Was desired.

図６にも示されるように、リングギヤ２８の内周縁部３８のうち径方向において開口３６に対向する部分、すなわち周壁２２の開口３６の回転軸線Ｃ１まわりの角度範囲内の部分は、周壁２２の開口３６の回転軸線Ｃ１まわりの角度範囲外の内周縁部３８に比べて、開口３６側に突出した内周側突出部４４を有している。
内周側突出部４４は、開口３６が周壁２２を貫通する方向から見たときに開口３６の一部を覆うように構成されており、開口３６の回転軸線Ｃ１まわりの角度範囲外であって開口３６の一部を覆わない内周縁部３８に比べて開口３６側へ突出して形成されている。上記リングギヤ２８の内周縁部３８のうち周壁２２の開口３６の回転軸線Ｃ１まわりの角度範囲内の部分は、リングギヤ２８の回転軸線Ｃ１に垂直で、且つピニオンピン３０の中心線に垂直な方向から見たときに、リングギヤ２８の周壁２２の開口３６と重なる部分を含んでいる。この一対の内周側突出部４４の内周側端面４６は、図３に示されるように、デフケース２６の一対の開口３６のそれぞれに所定の間隔ｄを有して設けられている。また、リングギヤ２８の周壁２２に形成された開口３６の回転軸線Ｃ１まわりの角度範囲内の内周側突出部４４の形成された部分の円錐面上には、リングギヤ２８の周壁２２に形成された開口３６の回転軸線Ｃ１まわりの角度範囲外の部分の円錐面上と同様の噛合歯１６が形成されており、その歯幅が歯幅ａから最大歯幅ｂに拡大されている。 As shown in FIG. 6, the portion of the inner peripheral edge 38 of the ring gear 28 that faces the opening 36 in the radial direction, that is, the portion within the angular range around the rotation axis C <b> 1 of the opening 36 of the peripheral wall 22, Compared to the inner peripheral edge 38 outside the angular range around the rotation axis C <b> 1 of the opening 36, the inner peripheral protrusion 44 protrudes toward the opening 36.
The inner peripheral protrusion 44 is configured to cover a part of the opening 36 when viewed from the direction in which the opening 36 penetrates the peripheral wall 22, and is outside the angular range around the rotation axis C <b> 1 of the opening 36. It is formed so as to protrude toward the opening 36 as compared with the inner peripheral edge 38 that does not cover a part of the opening 36. The portion of the inner peripheral edge 38 of the ring gear 28 within the angular range around the rotation axis C1 of the opening 36 of the peripheral wall 22 is perpendicular to the rotation axis C1 of the ring gear 28 and perpendicular to the center line of the pinion pin 30. When viewed, it includes a portion overlapping the opening 36 of the peripheral wall 22 of the ring gear 28. As shown in FIG. 3, the inner peripheral side end surfaces 46 of the pair of inner peripheral protrusions 44 are provided with a predetermined distance d in each of the pair of openings 36 of the differential case 26. Further, on the conical surface of the portion where the inner protrusion 44 is formed within the angular range around the rotation axis C1 of the opening 36 formed on the peripheral wall 22 of the ring gear 28, the peripheral wall 22 of the ring gear 28 is formed. The meshing teeth 16 similar to those on the conical surface of the portion outside the angular range around the rotation axis C1 of the opening 36 are formed, and the tooth width is expanded from the tooth width a to the maximum tooth width b.

図８は、リングギヤ２８をその回転軸線Ｃ１と垂直な面へ射影させた際の射影を例示する図であって、内周側突出部４４の内周側端面４６の形状を説明するための図である。内周側突出部４４は、その内周側端面４６の射影である直線Ｂ１が、リングギヤ２８の周壁２２に形成された開口３６の回転軸線Ｃ１まわりの角度範囲外の部分の円錐面上に形成された歯幅ａの噛合歯１６の内周縁の射影である円Ａとの交わる点Ｘおよび点Ｙと円Ａの中心すなわち回転軸線Ｃ１を示す点Ｏとをそれぞれ結ぶ２直線の成す角Ｄが１０度以上となり、且つ直線Ｂ１上の点Ｏとの距離が最も小さい点Ｅが、好適には、円Ａの半径の９７％の半径を有し且つ円Ａと同心の破線で示された円Ｆの内側となるように、内周縁部３８のうちのデフケース２６の開口３６の回転軸線Ｃ１まわりの角度範囲内の部分が開口３６側に突出させられて形成される。点Ｅは、点Ｏを通る直線ＸＹに直交する線と直線Ｂ１との交点である。このように形成された内周側突出部４４により、リングギヤ２８のうちデフケース２６の周壁２２の開口３６の回転軸線Ｃ１まわりの角度範囲内の径方向の幅寸法が増やされることから、リングギヤ２８とデフケース２６との組立体の剛性を充分に高くすることができる。なお、内周側突出部４４の内周側端面４６の射影の直線Ｂ１は点Ｏに対して対称位置に１対生じるところ、図８では、それらのうちの１つが省略されている。   FIG. 8 is a diagram illustrating the projection when the ring gear 28 is projected onto a plane perpendicular to the rotation axis C1, and is a diagram for explaining the shape of the inner peripheral end face 46 of the inner peripheral protrusion 44. It is. In the inner peripheral projection 44, a straight line B1 which is a projection of the inner peripheral end surface 46 is formed on a conical surface of a portion outside the angular range around the rotation axis C1 of the opening 36 formed in the peripheral wall 22 of the ring gear 28. An angle D formed by two straight lines connecting the point X and the point Y intersecting with the circle A, which is a projection of the inner peripheral edge of the meshing tooth 16 having the tooth width a, and the center of the circle A, that is, the point O indicating the rotation axis C1. A point E that is 10 degrees or more and has the smallest distance from the point O on the straight line B1 preferably has a radius of 97% of the radius of the circle A and is indicated by a broken line concentric with the circle A. A portion in the angular range around the rotation axis C1 of the opening 36 of the differential case 26 in the inner peripheral edge 38 is formed so as to protrude toward the opening 36 so as to be inside the F. Point E is the intersection of a line perpendicular to straight line XY passing through point O and straight line B1. The inner circumferential protrusion 44 formed in this way increases the radial width within the angular range around the rotational axis C1 of the opening 36 of the peripheral wall 22 of the differential case 26 of the ring gear 28. The rigidity of the assembly with the differential case 26 can be sufficiently increased. Note that one pair of projection straight lines B1 of the inner peripheral side end face 46 of the inner peripheral side protruding portion 44 is generated at a symmetrical position with respect to the point O. In FIG. 8, one of them is omitted.

上述のように、本実施例のディファレンシャル装置１０によれば、リングギヤ２８の内周縁部３８のうち、開口３６が貫通する方向から見たときに開口３６の一部を覆うように構成され、開口３６の一部を覆わない内周縁部３８に比べて開口３６側に突出した内周側突出部４４を有する。そのような内周側突出部４４を有するリングギヤ２８とデフケース２６との組立体において、リングギヤ２８のうち開口３６の回転軸線Ｃ１まわりの角度範囲内において開口３６の一部を覆う内周側突出部４４により径方向の幅寸法が増やされて剛性が高くされることから、リングギヤ２８のドライブピニオン１３との噛合面積が変化することによるギヤノイズが抑制される。また、リングギヤ２８の内周側突出部４４は、デフケース２６の開口３６側へ突出したものであるため、デフケース２６およびリングギヤ２８の組立体が大きくなることはない。このため、リングギヤ２８とデフケース２６との組立体の剛性が高くされるとともにディファレンシャル装置１０全体の小型化が達成される。   As described above, according to the differential device 10 of the present embodiment, the inner peripheral edge 38 of the ring gear 28 is configured to cover a part of the opening 36 when viewed from the direction through which the opening 36 penetrates. Compared with the inner peripheral edge portion 38 that does not cover a part of the inner peripheral portion 36, the inner peripheral protrusion portion 44 protrudes toward the opening 36. In the assembly of the ring gear 28 and the differential case 26 having such an inner peripheral protrusion 44, the inner peripheral protrusion that covers a part of the opening 36 within the angular range around the rotation axis C <b> 1 of the opening 36 of the ring gear 28. Since the radial width dimension is increased by 44 and the rigidity is increased, gear noise due to a change in the meshing area of the ring gear 28 with the drive pinion 13 is suppressed. Further, since the inner peripheral side protruding portion 44 of the ring gear 28 protrudes toward the opening 36 side of the differential case 26, the assembly of the differential case 26 and the ring gear 28 does not increase. For this reason, the rigidity of the assembly of the ring gear 28 and the differential case 26 is increased, and the overall size of the differential device 10 is reduced.

また、本実施例のディファレンシャル装置１０によれば、リングギヤ２８のデフケース２６の開口３６の回転軸線Ｃ１まわりの角度範囲内の内周側突出部４４が形成された部分の円錐面上の噛合歯１６の歯幅ｂは、リングギヤ２８のデフケース２６の開口３６の回転軸線Ｃ１まわりの角度範囲外の部分の円錐面上に形成された噛合歯１６の歯幅ａよりも拡大されている。このため、リングギヤ２８とドライブピニオン１３との噛合位置が内周側突出部４４の側へずれた場合でも、ドライブピニオン１３はリングギヤ２８の内周側突出部４４の歯幅ｂに拡大された噛合歯１６と噛合うことより、リングギヤ２８とドライブピニオン１３との噛合面積の低下が抑制されて、ギヤノイズの発生が低減される。また、リングギヤ２８のドライブピニオン１３との噛合面積の低下による噛合歯１６への単位面積当りの入力が大きくなることが抑制されることから、リングギヤ２８の耐久性を向上することができる。   Further, according to the differential device 10 of the present embodiment, the meshing teeth 16 on the conical surface of the portion where the inner peripheral protrusion 44 is formed within the angular range around the rotation axis C1 of the opening 36 of the differential case 26 of the ring gear 28. The tooth width b of the ring gear 28 is larger than the tooth width a of the meshing teeth 16 formed on the conical surface of the portion outside the angular range around the rotation axis C1 of the opening 36 of the differential case 26 of the ring gear 28. For this reason, even when the meshing position of the ring gear 28 and the drive pinion 13 is shifted to the inner peripheral side protruding portion 44, the drive pinion 13 is engaged with the tooth width b of the inner peripheral side protruding portion 44 of the ring gear 28 expanded. By meshing with the teeth 16, a reduction in meshing area between the ring gear 28 and the drive pinion 13 is suppressed, and generation of gear noise is reduced. In addition, since the input per unit area to the meshing teeth 16 due to the decrease in the meshing area of the ring gear 28 with the drive pinion 13 is suppressed, the durability of the ring gear 28 can be improved.

次に、本発明の他の実施例を説明する。なお、以下の実施例において、前記実施例と機能において実質的に共通する部分には同一の符号を付して詳しい説明を省略する。   Next, another embodiment of the present invention will be described. In the following embodiments, parts that are substantially the same in function as those of the above embodiments are denoted by the same reference numerals, and detailed description thereof is omitted.

本実施例のディファレンシャル装置４８は、リングギヤ５０の内周側突出部５２の形状が前述のリングギヤ２８に対して異なる以外は、前述の実施例１のディファレンシャル装置１０と共通する。以下、その異なる点について図９を用いて説明する。図９は、リングギヤ５０をその回転軸線Ｃ１と垂直な面へ射影させた際に生じる射影を示す図であって、図８に相当する図である。内周側突出部５２は、その円錐面上に形成された歯幅ｂの噛合歯１６の内周縁の射影である折れ線Ｂ２の円Ａとの交わる点Ｘおよび点Ｙと点Ｏとの間をそれぞれ結ぶ２直線の成す角Ｄが１０度以上、且つ折れ線Ｂ２上の点Ｏとの距離が最も小さい点Ｅが円Ｆの内側となるように、内周縁部３８のうちのデフケース２６の一対の開口３６の回転軸線Ｃ１まわりの角度範囲内の部分が開口３６側に突出して形成されている。本実施例の点Ｅは、点Ｏを通る直線ＸＹに直交する線と折れ線Ｂ２との交点である。折れ線Ｂ２は、その点Ｏを通る直線ＸＹに直交する線に対して、対称形状である。本実施例のディファレンシャル装置４８によれば、前述の実施例１と同様の効果を得ることができる。   The differential device 48 of the present embodiment is the same as the differential device 10 of the first embodiment described above except that the shape of the inner peripheral protrusion 52 of the ring gear 50 is different from that of the ring gear 28 described above. The different points will be described below with reference to FIG. FIG. 9 is a diagram showing a projection generated when the ring gear 50 is projected onto a plane perpendicular to the rotation axis C1, and corresponds to FIG. The inner peripheral side protruding portion 52 is formed between points X and Y and points O intersecting with the circle A of the polygonal line B2, which is a projection of the inner peripheral edge of the meshing teeth 16 of the tooth width b formed on the conical surface. A pair of differential cases 26 in the inner peripheral edge 38 is such that the point E having the smallest distance from the point O on the broken line B2 is 10 ° or more and the point E on the broken line B2 is the inner side of the circle F. A portion in the angular range around the rotation axis C1 of the opening 36 is formed to protrude toward the opening 36. The point E in the present embodiment is an intersection of a line perpendicular to the straight line XY passing through the point O and the broken line B2. The broken line B2 has a symmetrical shape with respect to a line orthogonal to the straight line XY passing through the point O. According to the differential device 48 of the present embodiment, the same effects as those of the first embodiment can be obtained.

図１０は、本実施例のディファレンシャル装置５４のリングギヤ５６を、その回転軸線Ｃ１と垂直な面へ射影させた際に生じる射影であって、図８に相当する図である。リングギヤ５６の内周側突出部５８は、その円錐面上に形成された歯幅ｂの噛合歯１６の内周縁の射影である滑らかな円弧Ｂ３の円Ａとの交わる点Ｘおよび点Ｙと点Ｏとの間をそれぞれ結ぶ２直線の成す角Ｄが１０度以上、且つ円弧Ｂ３上の点Ｏとの距離が最も小さい点Ｅが円Ｆの内側となるように、内周縁部３８のうちのデフケース２６の一対の開口３６の回転軸線Ｃ１まわりの角度範囲内の部分が開口３６側に突出して形成されている。本実施例の点Ｅは、点Ｏを通る直線ＸＹに直交する線と円弧Ｂ３との交点である。円弧Ｂ３は、その点Ｏを通る直線ＸＹに直交する線に対して対称形状である。本実施例のディファレンシャル装置５４によれば、前述の実施例１と同様の効果を得ることができる。   FIG. 10 is a projection generated when the ring gear 56 of the differential device 54 of this embodiment is projected onto a plane perpendicular to the rotation axis C1, and corresponds to FIG. The inner peripheral side protruding portion 58 of the ring gear 56 has a point X and a point Y that intersect with a circle A of a smooth arc B3 that is a projection of the inner peripheral edge of the meshing tooth 16 having a tooth width b formed on the conical surface. Of the inner peripheral edge 38 so that an angle D formed by two straight lines connecting with O is 10 degrees or more and the point E having the smallest distance from the point O on the arc B3 is inside the circle F. Portions in the angular range around the rotation axis C <b> 1 of the pair of openings 36 of the differential case 26 are formed to protrude toward the opening 36. The point E in the present embodiment is an intersection of a line perpendicular to the straight line XY passing through the point O and the arc B3. The arc B3 is symmetrical with respect to a line orthogonal to the straight line XY passing through the point O. According to the differential device 54 of the present embodiment, the same effects as those of the first embodiment can be obtained.

図１１は、本実施例のディファレンシャル装置６０のリングギヤ６２を、その回転軸線Ｃ１と垂直な面へ射影させた際に生じる射影であって、図８に相当する図である。リングギヤ６２の内周側突出部６４は、その円錐面上に形成された歯幅ｂの噛合歯１６の内周縁の射影である曲線Ｂ４の円Ａとの交わる点Ｘおよび点Ｙと点Ｏとを結ぶ２直線の成す角Ｄが１０度以上、且つ曲線Ｂ４上の点Ｏとの距離が最も小さい点Ｅが円Ｆの内側となるように、内周縁部３８のうちのデフケース２６の一対の開口３６の回転軸線Ｃ１まわりの角度範囲内の部分が開口３６側に突出して形成されている。本実施例のディファレンシャル装置６０によれば、前述の実施例１と同様の効果を得ることができる。   FIG. 11 is a projection generated when the ring gear 62 of the differential device 60 of this embodiment is projected onto a plane perpendicular to the rotation axis C1, and corresponds to FIG. The inner peripheral side protruding portion 64 of the ring gear 62 has points X, Y, and O that intersect with a circle A of a curve B4 that is a projection of the inner peripheral edge of the meshing teeth 16 of the tooth width b formed on the conical surface. Of the differential case 26 in the inner peripheral edge 38 so that the point E having the smallest distance from the point O on the curve B4 is on the inner side of the circle F. A portion in the angular range around the rotation axis C1 of the opening 36 is formed to protrude toward the opening 36. According to the differential device 60 of the present embodiment, the same effects as those of the first embodiment can be obtained.

以上、本発明を表及び図面を参照して詳細に説明したが、本発明は更に別の態様でも実施でき、その主旨を逸脱しない範囲で種々変更を加え得るものである。   As mentioned above, although this invention was demonstrated in detail with reference to the table | surface and drawing, this invention can be implemented in another aspect, and can be variously changed in the range which does not deviate from the main point.

たとえば、前述の実施例のディファレンシャル装置１０によれば、デフケース２６の周壁２２にピニオンピン３０を挟んで一対の開口３６を備えるものであったが、これに限定されるものではなく、たとえば１つの開口、あるいは３つ以上の開口３６が周壁２２に形成されて、リングギヤ２８の内周縁部３８のうちの開口３６の回転軸線Ｃ１まわりの角度範囲内の開口３６周辺部分が、開口３６の回転軸線Ｃ１まわりの角度範囲外の内周縁部３８に比べて上記１つあるいは３つ以上の開口３６側に突出されることにより形成された内周側突出部４４が設けられて、リングギヤ２８とデフケース２６との組立体の剛性が高められるように構成されてもよい。   For example, according to the differential device 10 of the above-described embodiment, the pair of openings 36 are provided on the peripheral wall 22 of the differential case 26 with the pinion pin 30 interposed therebetween. However, the present invention is not limited to this. An opening, or three or more openings 36 are formed in the peripheral wall 22, and the peripheral portion of the opening 36 within the angular range around the rotation axis C <b> 1 of the inner periphery 38 of the ring gear 28 is the rotation axis of the opening 36. An inner peripheral protrusion 44 formed by protruding toward the one or more openings 36 as compared with the inner peripheral edge 38 outside the angular range around C1 is provided, and the ring gear 28 and the differential case 26 are provided. And the rigidity of the assembly may be increased.

また、前述の実施例のディファレンシャル装置１０によれば、リングギヤ２８のデフケース２６の開口３６の回転軸線Ｃ１まわりの角度範囲内の内周側突出部４４の形成された部分の円錐面上の噛合歯１６の歯幅ｂは、リングギヤ２８のデフケース２６の開口３６の回転軸線Ｃ１まわりの角度範囲外の部分の円錐面上の噛合歯１６の歯幅ａよりも拡大されていたが、これに限定されるものではなく、たとえば、内周側突出部４４の形成された部分の円錐面上に形成される噛合歯１６が、リングギヤ２８のデフケース２６の開口３６の回転軸線Ｃ１まわりの角度範囲外の部分の円錐面上の噛合歯１６と同じ歯幅ａから最大歯幅ｂに拡大されずに、内周側突出部４４に完全な噛合歯１６が形成されずに不完全な形状の噛合歯１６が形成されるか、あるいは噛合歯が全く形成されないようにしてもよい。内周側突出部４４に噛合歯１６が形成されなくとも、リングギヤ２８とデフケース２６との組立体の剛性は向上される。   Further, according to the differential device 10 of the above-described embodiment, the meshing teeth on the conical surface of the portion where the inner peripheral protrusion 44 is formed within the angular range around the rotation axis C1 of the opening 36 of the differential case 26 of the ring gear 28. The tooth width b of the ring gear 28 is larger than the tooth width a of the meshing tooth 16 on the conical surface outside the angular range around the rotation axis C1 of the opening 36 of the differential case 26 of the ring gear 28, but is limited to this. For example, the meshing teeth 16 formed on the conical surface of the portion where the inner peripheral projection 44 is formed are portions outside the angular range around the rotation axis C1 of the opening 36 of the differential case 26 of the ring gear 28. The mesh teeth 16 on the conical surface 16 are not enlarged from the same tooth width a to the maximum tooth width b, and the mesh teeth 16 having an incomplete shape are formed without forming the complete mesh teeth 16 on the inner peripheral protrusion 44. Formed or Rui may be meshing teeth are not formed at all. Even if the meshing teeth 16 are not formed on the inner peripheral projection 44, the rigidity of the assembly of the ring gear 28 and the differential case 26 is improved.

また、前述の実施例のディファレンシャル装置１０によれば、デフケース２６の開口３６とそれに対向するリングギヤ２８の内周側突出部４４の内周側端面４６との間に、所定の間隔ｄを有するように構成されていたが、これに限定されるものではなく、たとえば、デフケース２６とリングギヤ２８とのボルト３４による組付時にデフケース２６に対してリングギヤ２８がほぼ相対回転不能な程度に、デフケース２６の開口３６と内周側突出部４４の内周側端面４６との間隔ｄが狭められてもよい。このようにすれば、デフケース２６に対してリングギヤ２８が周方向に位置決めされて、組み付ける際にリングギヤ２８がデフケース２６に対して回転することが抑制されるため、デフケース２６とリングギヤ２８とのボルト３４による組付けが容易となる。   Further, according to the differential device 10 of the above-described embodiment, a predetermined distance d is provided between the opening 36 of the differential case 26 and the inner peripheral side end face 46 of the inner peripheral side protruding portion 44 of the ring gear 28 opposed thereto. However, the present invention is not limited to this. For example, when the differential gear 26 and the ring gear 28 are assembled by the bolts 34, the differential gear 26 can be rotated relative to the differential case 26 so that the ring gear 28 is not relatively rotatable. The distance d between the opening 36 and the inner peripheral side end face 46 of the inner peripheral side protrusion 44 may be narrowed. In this way, the ring gear 28 is positioned in the circumferential direction with respect to the differential case 26, and the ring gear 28 is prevented from rotating with respect to the differential case 26 during assembly. Therefore, the bolt 34 between the differential case 26 and the ring gear 28 is provided. Assembling is easy.

また、前述の実施例のディファレンシャル装置１０によれば、デフケース２６とリングギヤ２８とは、ボルト３４によって組み付けられていたが、溶接によって組み付けられてもよい。このようにすれば、デフケース２６に対してリングギヤ２８がボルトによって位置決めされないため、デフケース２６とリングギヤ２８との組付けが容易となる。   Moreover, according to the differential apparatus 10 of the above-mentioned Example, although the differential case 26 and the ring gear 28 were assembled | attached with the volt | bolt 34, you may assemble | attach by welding. In this way, the ring gear 28 is not positioned by the bolt with respect to the differential case 26, so that the differential case 26 and the ring gear 28 can be easily assembled.

また、前述の実施例では、内周側突出部４４、内周側突出部５２、内周側突出部５８および内周側突出部６４は、歯幅ａの噛合歯１６の内周縁の射影である円Ａの９７％径の円Ｆよりも内側まで突出するものであったが、必ずしも円Ｆの内側まで突出するものでなくてもよく、突出量に応じた剛性向上効果を得ることができる。   Moreover, in the above-mentioned Example, the inner peripheral side protrusion part 44, the inner peripheral side protrusion part 52, the inner peripheral side protrusion part 58, and the inner peripheral side protrusion part 64 are projections of the inner peripheral edge of the meshing tooth 16 having the tooth width a. Although it protrudes to the inside of a circle F having a diameter of 97% of a certain circle A, it does not necessarily protrude to the inside of the circle F, and an effect of improving rigidity according to the amount of protrusion can be obtained. .

なお、上述したのはあくまでも一実施形態であり、その他一々例示はしないが、本発明は、その主旨を逸脱しない範囲で当業者の知識に基づいて種々変更、改良を加えた態様で実施することができる。   It should be noted that the above description is merely an embodiment, and other examples are not illustrated. However, the present invention is implemented in variously modified and improved modes based on the knowledge of those skilled in the art without departing from the gist of the present invention. Can do.

１０、４８、５４、６０：車両用ディファレンシャル装置
１６：噛合歯
１８：サイドギヤ
２０：ピニオンギヤ
２２：周壁
２４：フランジ部
２６：デフケース
２８、５０、５６、６２：リングギヤ
３０：ピニオンピン
３６：開口
３８：内周縁部
４０：外周縁部
４４、５２、５８、６４：内周側突出部（突出部）
Ｃ１：回転軸線
ａ：歯幅
ｂ：歯幅 10, 48, 54, 60: Vehicle differential device 16: Meshing tooth 18: Side gear 20: Pinion gear 22: Peripheral wall 24: Flange portion 26: Differential case 28, 50, 56, 62: Ring gear 30: Pinion pin 36: Opening 38: Inner peripheral edge 40: Outer peripheral edge 44, 52, 58, 64: Inner peripheral protrusion (protrusion)
C1: rotation axis a: tooth width b: tooth width

Claims (2)

一対のサイドギヤおよび該サイドギヤと噛合うピニオンギヤを収容する周壁と該周壁の一部に内外を貫通して形成された開口とを有し、一回転軸線まわりに回転させられるデフケースと、前記周壁の外側に装着され、前記回転軸線を中心とする円環状のリングギヤとを、備えた車両用ディファレンシャル装置において、前記リングギヤの内周縁部のうち、前記開口が貫通する方向から見たときに前記開口の一部を覆うように構成され、前記開口の一部を覆わない内周縁部に比べて前記開口側に突出した突出部を有することを特徴とする車両用ディファレンシャル装置。   A differential case that has a peripheral wall that houses a pair of side gears and a pinion gear that meshes with the side gear, and an opening that is formed through a part of the peripheral wall so as to penetrate the inside and outside of the peripheral gear; And a ring gear having an annular ring centered on the rotation axis, and a portion of the opening of the ring gear when viewed from a direction through which the opening penetrates the inner peripheral edge of the ring gear. The vehicle differential apparatus has a protruding portion that is configured to cover the opening and protrudes toward the opening as compared with an inner peripheral edge that does not cover a part of the opening. 前記リングギヤの歯幅は、前記突出部では、それ以外の部分よりも拡大されていることを特徴とする請求項１の車両用ディファレンシャル装置。
The differential gear for a vehicle according to claim 1, wherein a tooth width of the ring gear is larger in the protruding portion than in other portions.
JP2015157740A 2015-08-07 2015-08-07 Differential device for vehicle Active JP6269615B2 (en)

Priority Applications (8)

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JP2015157740A JP6269615B2 (en) 2015-08-07 2015-08-07 Differential device for vehicle
US15/220,831 US10012302B2 (en) 2015-08-07 2016-07-27 Vehicle differential
MYPI2016702756A MY183853A (en) 2015-08-07 2016-07-28 Vehicle differential
BR102016017652A BR102016017652A2 (en) 2015-08-07 2016-07-29 vehicle differential
KR1020160098398A KR101846691B1 (en) 2015-08-07 2016-08-02 Vehicle differential
CN201610633149.2A CN106438922B (en) 2015-08-07 2016-08-04 differential device for vehicle
EP16182671.4A EP3128208B1 (en) 2015-08-07 2016-08-04 Vehicle differential
RU2016132132A RU2638341C1 (en) 2015-08-07 2016-08-04 Differential of vehicle

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EP3128208A3 (en) 2017-02-22
BR102016017652A2 (en) 2017-02-14
US20170037950A1 (en) 2017-02-09
KR101846691B1 (en) 2018-05-18
RU2638341C1 (en) 2017-12-13
MY183853A (en) 2021-03-17
JP2017036780A (en) 2017-02-16
KR20170017755A (en) 2017-02-15
US10012302B2 (en) 2018-07-03
CN106438922B (en) 2018-11-09
EP3128208A2 (en) 2017-02-08
CN106438922A (en) 2017-02-22

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